EP3092411B1 - Procédé permettant d'empêcher la présence de condensat dans l'huile d'un compresseur à injection d'huile et compresseur dans lequel un tel procédé est appliqué - Google Patents

Procédé permettant d'empêcher la présence de condensat dans l'huile d'un compresseur à injection d'huile et compresseur dans lequel un tel procédé est appliqué Download PDF

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Publication number
EP3092411B1
EP3092411B1 EP15710412.6A EP15710412A EP3092411B1 EP 3092411 B1 EP3092411 B1 EP 3092411B1 EP 15710412 A EP15710412 A EP 15710412A EP 3092411 B1 EP3092411 B1 EP 3092411B1
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EP
European Patent Office
Prior art keywords
oil
compressor
pressure
temperature
compressor element
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Application number
EP15710412.6A
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German (de)
English (en)
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EP3092411A1 (fr
Inventor
Andries Jan F Desiron
VOCHT Alexander DE
Joeri COECKELBERGS
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Atlas Copco Airpower NV
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Atlas Copco Airpower NV
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Priority claimed from BE2014/0095A external-priority patent/BE1021804B1/nl
Application filed by Atlas Copco Airpower NV filed Critical Atlas Copco Airpower NV
Priority to EP19164967.2A priority Critical patent/EP3534008B1/fr
Priority to EP21174028.7A priority patent/EP3889433A1/fr
Publication of EP3092411A1 publication Critical patent/EP3092411A1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/06—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids specially adapted for stopping, starting, idling or no-load operation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/06—Control using electricity
    • F04B49/065—Control using electricity and making use of computers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/021—Control systems for the circulation of the lubricant
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B19/00—Machines or pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B1/00 - F04B17/00
    • F04B19/08—Scoop devices
    • F04B19/12—Scoop devices of helical or screw-type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F04B49/24—Bypassing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/02—Liquid sealing for high-vacuum pumps or for compressors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0007—Injection of a fluid in the working chamber for sealing, cooling and lubricating
    • F04C29/0014—Injection of a fluid in the working chamber for sealing, cooling and lubricating with control systems for the injection of the fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/026—Lubricant separation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2201/00—Pump parameters
    • F04B2201/04—Carter parameters
    • F04B2201/0402—Lubricating oil temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/19—Temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16N—LUBRICATING
    • F16N29/00—Special means in lubricating arrangements or systems providing for the indication or detection of undesired conditions; Use of devices responsive to conditions in lubricating arrangements or systems
    • F16N29/02—Special means in lubricating arrangements or systems providing for the indication or detection of undesired conditions; Use of devices responsive to conditions in lubricating arrangements or systems for influencing the supply of lubricant

Definitions

  • the present invention relates to a method for preventing condensate in the oil of an oil-injected compressor.
  • the invention is intended for oil-injected compressors with a variable speed.
  • Such compressors comprise a compressor element, for example in the form of a screw compressor element with two meshed rotor screws that are mounted on bearings in a housing and which are driven by a drive with a variable speed that is a function of the load.
  • Such compressors are further provided with an oil circuit that is provided to inject oil into the compressor element for lubricating and cooling the rotor screws and for sealing the clearance between the rotors themselves and between the rotors and the housing.
  • the injected oil leaves the compressor element as a mist of oil droplets in the compressed gas, which, before being supplied to the consumer network, is driven through an oil separator to separate and receive the oil and to inject the oil, optionally after cooling, back into the compressor element.
  • Known compressors of this type comprise a controller to control the speed as a function of the demanded flow rate and the demanded pressure in the downstream consumer network.
  • the aforementioned controller ensures that the compressor element is stopped according to a specified stop program whereby the speed of the compressor element decreases to a set minimum speed and whereby, when this minimum speed is reached, the drive of the compressor element is switched off.
  • the compressed gas that leaves the compressor element and is driven through the oil separator also contains a quality of water vapour in addition to oil droplets.
  • a disadvantage is that there is a risk that when the temperature of the compressed gas at the outlet of the compressor element is not high enough, for example with a low load and when the compressor element is stopped, the water vapour in the compressed gas will condense and get in the oil which can lead to damage when the compressor element is restarted.
  • the document EP 1 937 977 discloses a method for controlling a compressor regarding as reference value the temperature of the compressed gas as claimed in the preamble of claim 1.
  • the purpose of the present invention is to provide a solution to the aforementioned disadvantage and other disadvantages.
  • the invention concerns a compressor comprising an oil-injected compressor element with an inlet that can be closed by means of a controlled inlet valve and an outlet ; a drive for the compressor element; an oil circuit comprising an oil separator with an input that is connected to the outlet of the compressor element and an output to which a consumer network for compressed gas can be connected, whereby this oil separator comprises a pressure vessel in which the oil separated from the compressed gas is collected and from where oil can be injected into the compressor element via an injection pipe; a pressure sensor for determining the pressure in the consumer network and a controller for the drive of the compressor element that is such that when the pressure in the consumer network has reached a set maximum value, the drive of the compressor element is stopped according to a set stop program, with the characteristic that the compressor is provided with a temperature probe for determining the temperature of the compressed gas, and a 'recirculation pipe' that connects the oil separator to the inlet of the compressor element and in which a throttle and a controlled normally closed closable recirculation valve is incorporated
  • the compressor element is not immediately stopped when the set operating pressure in the consumer network has been reached, as is usually the case, but it is first checked whether the temperature of the oil in the pressure vessel is sufficient so as not to have condensate in the oil, and when the temperature is insufficient a recirculation program is first completed during which the compressor element continues running at a minimum speed in order to continue compressing gas, which after compression is guided from the pressure vessel to the inlet of the compressor element in order to be compressed again from there.
  • the stop program is completed in order to stop the compressor in the usual way, if need be with a certain delay during which the compressor element continues to run in recirculation to ensure homogeneous heating of the oil.
  • the minimum temperature above which there is no further risk of condensate in the oil primarily depends on the condensation temperature. The higher the set minimum temperature, the lower the risk of the presence of condensate in the oil.
  • the value of the minimum temperature is in all respects set at a fixed or calculated value that is lower than the temperature to which the thermostatic valve is set, which is generally present and which ensures that when the oil is cold, for example when starting up, the oil is injected directly into the compressor element and when the oil is warm, the oil is first guided around from the pressure tank along an oil cooler.
  • a minimum temperature is set that is as high as possible but lower than the temperature of the thermostatic valve, at least insofar there is a thermostat, whereby in practice this temperature is between 60°C and 90°C, for example around 70°C.
  • the minimum temperature can also be determined in real time on the basis of the condensation temperature, which can be calculated on the basis of the measured ambient temperature and relative humidity in real time for example. Protection built into the recirculation program ensures that if the desired minimum temperature cannot be reached, the compressor will nonetheless be stopped after a set minimum period.
  • Another protection facility ensures that if the oil heats up too quickly during the recirculation program, the drive is immediately stopped when a set maximum temperature is reached.
  • the compressed gas is recirculated over a calibrated throttle during the recirculation program in order to obtain a pressure in the pressure vessel that is lower than the pressure to which the minimum pressure valve of the pressure vessel is set in order to prevent compressed gas being supplied to the consumer network at this stage on the one hand, and so that a minimum internal pressure is guaranteed for oil injection to the compressor element on the other.
  • FIG. 1 concerns an oil-injected screw compressor 1 according to the invention, comprising a compressor element 2 of the known screw type with a housing 3 in which two meshed helical rotors 4 are driven by means of a drive 5.
  • the compressor element 2 is provided with an inlet 6 that can be closed by means of a controllable inlet valve 7, whereby this inlet 6 is connected to an inlet filter 9 by means of an intake pipe 8 to draw in gas, in this case air, from the environment.
  • the compressor element 2 is also provided with an outlet 10 and a pressure pipe 11 connected thereto that is connected to a downstream consumer network 16 via a pressure vessel 12 of an oil separator 13 and via a pressure pipe 14 and a cooler 15 for the supply of various pneumatic tools or similar that are not shown here.
  • a minimum pressure valve 17 is affixed in the pressure pipe 14 that only opens when the pressure in the pressure vessel 12 reaches a set minimum value pmin.
  • a release branch 18 is provided in the pressure vessel 12 that opens out at the location of the inlet 6 and which can be closed by means of a release valve 19 in the form of a spring-loaded controllable electric valve that is normally kept closed by means of a spring.
  • the screw compressor 1 is provided with an oil circuit 20 to inject oil 21 into the compressor element 2 from the pressure vessel 12 under the influence of the pressure in the pressure vessel 12 via a lifting pipe 22 in the pressure vessel 12 and injection pipe 23 for lubrication and/or cooling and/or sealing between the rotors 4 themselves and the rotors 4 and the housing 3.
  • the oil 21 that is driven from the pressure vessel 12 to the injection pipe 23 can be guided around through an oil cooler 27 via an oil filter 24 and thermostatic valve 25 via a branch pipe 26 to cool the oil 21 from the pressure vessel 12.
  • the cooled oil is guided over the drive 5 before being injected into the compressor element 2 in order to cool this drive 5.
  • the drive 5 is a drive with a variable speed n that is controlled as a function of the load of the consumer network 16, more specifically as a function of the pressure and the flow of gas taken off by the consumer network 16.
  • This drive 5 is controlled in a known way by an electrical or electronic controller 28 as a function of the aforementioned pressure in the consumer network 16, whereby this pressure is determined by means of a pressure sensor 29 or similar for example.
  • the controller 28 also ensures the control of the opening and closing of the release valve 19.
  • the compressor 1 is also equipped with a recirculation pipe 31 that connects the pressure tank 12 to the inlet 6 of the compressor element 2 and which can be closed by means of a recirculation valve 31, in this case in the form of a controlled spring-loaded normally closed electric valve.
  • a calibrated throttle 32 that is calculated in order to have a pressure in the pressure tank 12, when the recirculation valve 31 is opened, that is lower than the minimum pressure pmin to which the minimum pressure valve 17 is set.
  • This recirculation valve 31 is connected to the controller 28 to control the recirculation valve 31, primarily as a function of the pressure p measured by the aforementioned pressure sensor 29 and as a function of the temperature T of the compressed gas at or in the outlet 10 of the compressor element 2, whereby this temperature T is measured for example using a temperature sensor 33 whose signal is fed back to the controller 28.
  • the compressor 1 When starting up the drive 5 the compressor 1 is in a starting situation as shown in figure 1 , whereby the inlet valve 7 is open and the release valve 19 and the recirculation valve 31 are both in a closed state in order to close off the release pipe 18 and the recirculation pipe 30.
  • the pressure tank 12 is then partially filled with oil 21.
  • the pressure in the pressure vessel 12 then starts to rise and ensures that oil 21 is injected from the pressure tank 12 via the injection pipe 23 into the compressor element 2, whereby the oil, depending on the temperature of the oil and the position of the thermostatic valve 25, is driven directly to the injection pipe 23 in order to be diverted via the oil cooler 27.
  • the thermostatic valve 25 is set to a temperature T25 of 70°C for example.
  • the oil present in the compressed air is separated in the oil separator 13 and collected in the pressure tank 12.
  • the minimum pressure valve 17 opens and compressed air is supplied to the consumer network, after prior cooling in the cooler 15.
  • the pressure p in the consumer network is measured with the pressure probe 29 from which the signal is connected to the controller 28.
  • the controller 28 gives a signal to stop the drive according to a specified stop program. 34.
  • the speed n of the drive is slowed to a minimum set speed nmin and the drive is completely stopped as soon as this minimum speed nmin has been reached, whereby this speed is for example between 0 and 10,000 revolutions per minute, for example 2,100 revolutions per minute.
  • step B the pressure p in the consumer network is measured repeatedly or continuously and compared to the set maximum pressure pmax, after which as soon as the pressure p becomes greater than pmax, the stop program is started in step C.
  • an additional recirculation program 35 runs between step B and step C, as schematically shown in figure 3 .
  • This recirculation program 35 is thus started as soon as the pressure p is equal to pmax.
  • step D the temperature T is continuously or repetitively measured and compared to the set minimum temperature Tmin, above which there is no risk of condensate in the oil.
  • the compressor element 2 thus continues to compress air at a minimum speed, whereby this compressed air is fed back from the pressure vessel 12 via the recirculation pipe 18 and the throttle 32 to the inlet 6 where it is again drawn in and compressed by the compressor element 2.
  • the throttle is calculated so that in this phase a pressure is realised in the pressure tank 12 that is less than the pressure value pmn to which the minimum pressure valve is set, so that no compressed air can escape to the consumer network.
  • step D the step C is taken to start the stop program 34, as with a conventional compressor without recirculation.
  • the temperature T that is used for the recirculation program is preferably the temperature of the compressed gas that is measured or determined at the outlet of the compressor element.
  • the temperature in the outlet above which there is no or a minimal risk of the presence of condensate in the oil depends on the condensation temperature, which depends on the environmental variables in which the compressor 1 is operated.
  • Tmin The higher the set temperature Tmin the lower the risk. In every case Tmin must be lower than the temperature T25 to which the thermostatic valve 25 is set, at least insofar a thermostatic valve 25 is present, so that during the recirculation phase to warm up the oil the oil is not driven over the oil cooler 27.
  • the minimum temperature Tmin is then preferably set as close as possible below the aforementioned temperature T25 to which the thermostatic valve 25 is set, for example just below 70°C.
  • Tmin is between 60°C and 90°C.
  • thermostatic valve 25 the compressor can also be equipped with an electronically controlled mixer tap, in which case the temperature to which the thermostatic valve 25 is set does not need to be taken into account.
  • Figure 5 shows a diagram such as that of figure 3 , but with additional protection as explained hereinafter.
  • a maximum period tmax for the recirculation program is set in the controller 28. As long as the minimum temperature Tmin has not been reached, during the method step F it is checked whether the duration of the recirculation program 35 since the start of the reticulation program 35 has not exceeded the set maximum period.
  • the aforementioned maximum period tmax is set between 0 and 40 minutes for example, preferably approximately 600 seconds.
  • step G If during the recirculation program the temperature T does reach the set value Tmin, then as of then a timer is started that records the time t' since reaching Tmin, and which in step G lets the recirculation program continue for a set minimum period t'min before stopping the drive 5 in step C, in order to ensure uniform heating of the oil 21 in the pressure vessel 12.
  • the aforementioned minimum period t'min is set between 0 and 60 seconds for example, preferably approximately 10 seconds.
  • step H the temperature T is further monitored and the drive 5 is immediately stopped when a set maximum temperature Tmax is reached or exceeded that is higher than Tmin, in the event that the temperature T rises too quickly and the compressor cannot be stopped in time. This is shown by step H in figure 5 .
  • the set maximum temperature Tmax is set to a value that is between 5°C and 20°C higher than the aforementioned set minimum temperature Tmin for example, preferably to a value that is approximately 10°C higher than this set minimum temperature Tmin, and thus 80°C for example.
  • the drive 5 can only be switched off with a certain stop delay ⁇ t after the closing of the recirculation valve 31.
  • the drive 5 then continues to run at the minimum speed nmin during this stop delay ⁇ t, whereby this delay is between 0 and 40 seconds, preferably approximately 2 seconds.
  • this stop delay ⁇ t is to ensure that sufficient pressure is built up in the pressure vessel 12 to be able to act as a control pressure in order to be able to close the inlet valve 7 as usual.
  • the controller 28 after closing the recirculation valve 31 and before the drive 5 is switched off, the controller 28 first checks whether the temperature T is higher than the set minimum temperature Tmin and if not opens the release valve 19 to remove the evaporated condensate from the compressor 1.
  • An additional protection can consist of immediately stopping the compressor if the pressure p in the consumer network 16 goes above a set value pstop that is set higher than the aforementioned value pmax, which can occur for example when the recirculation valve 31 is blocked, in which case the air will not be able to be recirculated and will thereby be able to escape via the minimum pressure valve 17 to the consumer network, such that the pressure p in the consumer network 16 could unintentionally rise above pmax.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Computer Hardware Design (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compressor (AREA)

Claims (1)

  1. Compresseur du type à injection d'huile comprenant un élément (2) faisant office de compresseur du type à injection d'huile comprenant une entrée (6) qui peut être fermée au moyen d'une soupape d'entrée commandée (7), ainsi qu'une sortie (10) ; une commande (5) pour l'élément (2) faisant office de compresseur; un circuit d'huile (20) comprenant un séparateur d'huile (13) comprenant une entrée qui est reliée à la sortie (10) de l'élément (2) faisant office de compresseur et une sortie à laquelle un réseau de consommateur (16) pour du gaz sous pression peut être raccordé ; dans lequel ce séparateur d'huile (13) comprend un récipient sous pression (12) qui reçoit l'huile (21) séparée par rapport au gaz sous pression et à partir duquel de l'huile peut être injectée dans l'élément (2) faisant office de compresseur via le conduit d'injection (23) ; un capteur de pression (29) destiné à déterminer la pression (p) régnant dans le réseau de consommateur (16) et un contrôleur (28) pour la commande (5) de l'élément (2) faisant office de compresseur, qui est tel que, lorsque la pression (p) régnant dans le réseau de consommateur (16) a atteint une valeur maximale réglée (pmax), la commande (5) de l'élément (2) faisant office de compresseur est stoppée conformément à un programme d'arrêt réglé (34) ; caractérisé en ce que le compresseur (1) est muni d'une sonde de la température (33) destinée à déterminer la température (T) du gaz sous pression, et un « conduit de remise en circulation » (30) qui relie le séparateur d'huile (13) à l'entrée (6) de l'élément (2) faisant office de compresseur et dans lequel sont incorporés un étrangleur (32) et une soupape réglée de remise en circulation (31) apte à être fermée, normalement fermée, qui est reliée au contrôleur susmentionné (28) d'une manière telle qu'avant la mise à l'arrêt de la commande (5) de l'élément (2) faisant office de compresseur lorsque la pression maximale (pmax) dans le réseau de consommateur (16) a été atteinte, la soupape de remise en circulation (31) s'ouvre lorsque la température (T) déterminée par la sonde de température (33) est inférieure à une valeur minimale réglée (Tmin) et la commande (5) poursuit son entraînement jusqu'à ce que la température (T) atteigne la valeur minimale (Tmin) ou jusqu'à ce qu'un laps de temps maximal réglé (tmax) se soit écoulé pour pouvoir ensuite mettre à l'arrêt la commande (5), avec un retard (t'min).
EP15710412.6A 2014-01-10 2015-01-08 Procédé permettant d'empêcher la présence de condensat dans l'huile d'un compresseur à injection d'huile et compresseur dans lequel un tel procédé est appliqué Active EP3092411B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP19164967.2A EP3534008B1 (fr) 2014-01-10 2015-01-08 Procédé permettant d'empêcher la présence de condensat dans l'huile d'un compresseur à injection d'huile et compresseur dans lequel un tel procédé est appliqué
EP21174028.7A EP3889433A1 (fr) 2014-01-10 2015-01-08 Procédé permettant d'empêcher la présence de condensat dans l'huile d'un compresseur à injection d'huile et compresseur dans lequel un tel procédé est appliqué

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US201461925902P 2014-01-10 2014-01-10
BE2014/0095A BE1021804B1 (nl) 2014-01-10 2014-02-13 Werkwijze voor het voorkomen van condensaat in de olie van een oliegeinjecteerde compressor en compressor waarin zulke werkwijze wordt toegepast.
PCT/BE2015/000002 WO2015103678A1 (fr) 2014-01-10 2015-01-08 Procédé permettant d'empêcher la présence de condensat dans l'huile d'un compresseur à injection d'huile et compresseur dans lequel un tel procédé est appliqué

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EP21174028.7A Division EP3889433A1 (fr) 2014-01-10 2015-01-08 Procédé permettant d'empêcher la présence de condensat dans l'huile d'un compresseur à injection d'huile et compresseur dans lequel un tel procédé est appliqué
EP19164967.2A Division EP3534008B1 (fr) 2014-01-10 2015-01-08 Procédé permettant d'empêcher la présence de condensat dans l'huile d'un compresseur à injection d'huile et compresseur dans lequel un tel procédé est appliqué
EP19164967.2A Division-Into EP3534008B1 (fr) 2014-01-10 2015-01-08 Procédé permettant d'empêcher la présence de condensat dans l'huile d'un compresseur à injection d'huile et compresseur dans lequel un tel procédé est appliqué

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EP3092411B1 true EP3092411B1 (fr) 2019-05-22

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EP19164967.2A Active EP3534008B1 (fr) 2014-01-10 2015-01-08 Procédé permettant d'empêcher la présence de condensat dans l'huile d'un compresseur à injection d'huile et compresseur dans lequel un tel procédé est appliqué
EP21174028.7A Withdrawn EP3889433A1 (fr) 2014-01-10 2015-01-08 Procédé permettant d'empêcher la présence de condensat dans l'huile d'un compresseur à injection d'huile et compresseur dans lequel un tel procédé est appliqué
EP15710412.6A Active EP3092411B1 (fr) 2014-01-10 2015-01-08 Procédé permettant d'empêcher la présence de condensat dans l'huile d'un compresseur à injection d'huile et compresseur dans lequel un tel procédé est appliqué

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EP21174028.7A Withdrawn EP3889433A1 (fr) 2014-01-10 2015-01-08 Procédé permettant d'empêcher la présence de condensat dans l'huile d'un compresseur à injection d'huile et compresseur dans lequel un tel procédé est appliqué

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EP (3) EP3534008B1 (fr)
JP (1) JP6543634B2 (fr)
KR (1) KR101981847B1 (fr)
CN (2) CN204783653U (fr)
ES (1) ES2888652T3 (fr)
WO (1) WO2015103678A1 (fr)

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BE1024700B1 (nl) * 2016-10-25 2018-06-01 Atlas Copco Airpower Naamloze Vennootschap Regelaar voor het regelen van de snelheid van een motor die een oliegeïnjecteerde compressor aandrijft en werkwijze voor het regelen van die snelheid
US11085448B2 (en) * 2017-04-21 2021-08-10 Atlas Copco Airpower, Naamloze Vennootschap Oil circuit, oil-free compressor provided with such oil circuit and a method to control lubrication and/or cooling of such oil-free compressor via such oil circuit
JP7146478B2 (ja) * 2018-06-22 2022-10-04 株式会社神戸製鋼所 スクリュー圧縮機及びガス圧縮システム
US11207618B2 (en) * 2018-08-21 2021-12-28 Rocky Mountain Filtration Solutions, Inc. Portable lubricant filtration tool and methods of use
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JPS5888489A (ja) 1981-11-20 1983-05-26 Tokico Ltd 油冷式圧縮機
US5318151A (en) 1993-03-17 1994-06-07 Ingersoll-Rand Company Method and apparatus for regulating a compressor lubrication system
DE4313573A1 (de) 1993-04-26 1994-10-27 Leobersdorfer Maschf Verringerung der Kondensation von Wasserdampf und Austreiben von Kondensat während der Kompression von Luft
JPH08219024A (ja) 1995-02-14 1996-08-27 Iwata Air Compressor Mfg Co Ltd 油冷式圧縮機のドレン水除去方法ならびに装置
JPH08319976A (ja) * 1995-05-25 1996-12-03 Hitachi Ltd 油冷式空気圧縮機
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EP1937977A1 (fr) * 2005-10-21 2008-07-02 Atlas Copco Airpower, Naamloze Vennootschap Dispositif pour empecher la formation de condensat dans un gaz comprime et groupe compresseur equipe dudit dispositif
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EP3092411A1 (fr) 2016-11-16
KR20160108439A (ko) 2016-09-19
EP3534008B1 (fr) 2021-06-23
EP3534008A1 (fr) 2019-09-04
JP2017504754A (ja) 2017-02-09
CN204783653U (zh) 2015-11-18
CN104776028A (zh) 2015-07-15
ES2888652T3 (es) 2022-01-05
WO2015103678A1 (fr) 2015-07-16
US10550844B2 (en) 2020-02-04
KR101981847B1 (ko) 2019-05-23
JP6543634B2 (ja) 2019-07-10
US20160327045A1 (en) 2016-11-10
EP3889433A1 (fr) 2021-10-06
CN104776028B (zh) 2017-08-29

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